DE60320174T2 - Printing speed-dependent jaw adjustment system for a jaw cylinder in the folding device of a web-fed rotary printing press - Google Patents

Description

BACKGROUND OF THE INVENTION

Field of the invention

These The invention relates to a folding station attached to a web-fed rotary printing press added is, for example, in newspaper production, for cutting the printed paper web in sections and folds of successive Track sections around their middle to the shape of signatures. Especially the invention relates to a jaw cylinder on the folding device, the sentences consisting of fixed and movable jaws, which are on the periphery at intervals from each other, has, for folding the web sections, when pressed into the jaw cavities. In particular, it concerns the invention a system for automatically adjusting the spacing between the fixed and the movable jaws accordingly the working speed of the printing machine.

Description of the state of technology

The to be detected by the jaws on the jaw cylinder Web sections are subject to substantial changes in thickness, even in the restricted Case of newspaper production. Also the thickness of the paper used itself can be different. In addition, the number can vary greatly from the side of each sheet to be produced, if two or more webs are printed simultaneously and on top of each other before they can be used to produce multi-page signatures Folding station are introduced. The spacing between each set of solid and movable Folding flap needs to adapt to these widely varying thicknesses be foldable web sections adjustable to produce suitable folds, without damage the printed paper. However, you have to the jaws capture the track sections firmly enough to unintentional detach to prevent, when the web sections afterwards folded into signatures become.

The Japanese Patent Publication No. 7-55761 is hereby acknowledged as prior art with respect to the subject of the jaw spacing adjustment. It teaches to detect the thickness of the printed web or webs being fed into the folder and to vary the spacing between the fixed and movable folders accordingly.

In the younger ones However, the past has such a thickness-dependent attitude the jaw spacing for the correct functioning of the jaw cylinder due to considerable Increase in the operating speed of the printing machine proved to be inadequate. Let's assume that the jaw spacing is now for a particular Web thickness and at a certain operating speed of the printing press is set appropriately. In this case it happened according to the thickness-dependent attitude the jaw spacing of the prior art easily that the web sections fell off the jaws when the Printing press speed has been increased, especially in the Case of the production of multi-page signatures.

Turn Let us now briefly the construction of the folding station of the rotary printing machine to know more about the To experience problems with the jaw spacing adjustment occur. The folding station has next to the jaw cylinder a Cutting cylinder and a folding cylinder on, with all cylinders while of the progressive printing process are in constant rotation. The printed paper web is first around a part of the folding cylinder laid and while she over this is moved by cutting blades on the cutting cylinder, the over the web is held against the folding cylinder, in successive Sections cut. The folding cylinder is elongated Folding knives fitted, each parallel to the folding cylinder axis extend and arranged at the periphery at intervals from each other are. Each folding blade is movable radially to the folding cylinder.

Each track portion is pushed away from the surface of the folding cylinder by one of the folding blades, and its central portion is inserted into one of the elongated jaw cavities which are cut at intervals around the circumference in the surface of the jaw cylinder. The central portion of the web portion which has been pressed into the jaw cavity is therein caught together with the folding blade between the fixed and the movable jaw when the movable jaw is closed against the fixed jaw and thereby folded about the centerline of the web portion. Thereafter, the web section is guided by the jaw cylinder away from the surface of the folding cylinder as these cylinders continue to rotate in opposite directions. The folding blade moves between the fixed and the movable jaw, immediately after the web portion has been detected by this, so that the web portion is folded along the center line, while being guided away from the folding cylinder.

If the web section is pulled away from the folding cylinder as above, after its middle part has been caught by the jaws, must the front half the web portion are moved into sliding contact with the folding cylinder. An inertial force then acts on the track section and tends, contrary to the spring pressure, which exerted on the jaws is, the track section except To engage with the jaws. The larger the mass of the web section or the bigger the Number of superimposed Railways is the stronger is the centrifugal action of the web section. In fact, they fell in the worst case, the web sections from the jaws.

obvious solutions for this Problem could to make the Falzklappenbeabstandung narrower, heavier springs for the moving To use jaws or both. These solutions are not satisfactory because it is at lower operating speeds of the printing press to ink transfer between the touching ones surfaces the folded track sections would come.

BRIEF SUMMARY OF THE INVENTION

The The present invention aims to provide in connection with the folding station a rotary press, the jaw spacing automatically to adjust to the operating speed of the printing press, to the risk of unintentional detachment of the track sections the jaws and of ink transfer between each other touching surfaces to minimize.

A Another object of the invention is the automatic adjustment of Jaw spacing not only from the operating speed depending on the printing press but also of the mass of each section of track to be folded or the sides of the signatures to be produced.

Zugesammengefasst The present invention relates to a speed-dependent jaw spacing adjustment system for one Jaw cylinder at the folding station of a web-fed rotary printing press, where one or more sheets of printed paper in successive Sections are cut and each track section to a sheet is folded. The jaw cylinder is conventionally fixed and a movable jaw equipped, the latter can be moved to the former and away from it, to capture and folding each web section with its middle part in between introduced becomes. The fixed and the movable jaw are beyond separate, independent mounted movable parts of the jaw cylinder, which means with jaw spacing adjustment means are coupled to the setting of the spacing in between any operating phase of the movable jaw relative to allow for the fixed jaw. The jaw spacing adjustment means have their own Drive means comprising a bidirectional electric drive motor, for example, a stepper motor on.

To the Drive motor controllable food with power according to the Operating speed of the printing machine includes the jaw spacing control system a printing machine speed circuit for providing a Press speed signal indicating the speed with which the web is currently being fed into the folding station, and a jaw spacing circuit for providing a Jaw spacing signal representing the current actual spacing between indicates the fixed and the movable jaw. With these circuits connected is a jaw spacing adjustment circuit, that in response to the upcoming press speed signal and the jaw spacing signal is a jaw spacing adjustment signal for adjusting the jaw spacing according to the current one Print engine speed outputs. The exit of the jaw spacing adjustment circuit is connected to the drive motor for the jaw spacing adjustment means dependent on from the jaw spacing adjustment signal.

In particular, the jaw spacing adjustment circuitry is responsive to the upcoming press speed signal by determining optimum jaw spacing for the current press speed and comparing that optimum jaw spacing to the actual jaw spacing indicated by the jaw spacing signal. If it turns out that there is a difference between the desired and actual jaw spacing, then he The adjustment circuit generates the jaw spacing adjustment signal to eliminate this difference or reduce it to an allowable range.

Preferably can in cases in which the printing press for the simultaneous printing of a variable number of webs for the production of printed sheets designed with a variable number of sides, the jaw spacing not just according to the press speed, but also according to the number of webs to be processed together be set. For this purpose, furthermore, an input device for entering data indicating how many lanes at a time processed, and a memory for storing a table, the desired Falzklappenbeabstandungen for different combinations from a series of different press speeds and a number of different numbers of lanes provided become. By entering the lane number data in addition to the press speed signal and the actual jaw spacing signal may be the jaw spacing adjustment circuit be caused, the desired Falzklappenbeabstandung to read from the memory, which for the concrete combination from the current press speed and the current Number of lanes is suitable.

Therefore at whatever speed the press is operating is, the Falzklappenbeabstandung for detecting and folding the web sections with optimum pressure automatically according to this printing machine speed set. The track sections with any of various given thicknesses allowed at high press speed not inadvertently from the jaws fall, nor may it between their touching each other surfaces at low press speed for ink transfer come. All in all, it has been found that the jaw spacing adjustment system Significantly to the production of prints of consistently high quality and too contributes to the reduction of press downtimes.

By the lecture the following description and the appended claims in conjunction with the accompanying drawings, which is the preferred embodiment invention, the above and other objects, Features and advantages of this invention illustrated and the invention itself will be better understood.

BRIEF DESCRIPTION OF THE DRAWINGS

1 Fig. 12 is a schematic view of a folding station of a web-fed rotary printing press including a jaw cylinder to which the present invention is applicable;

2 FIG. 12 is a fragmentary, developed sectional view (taken along the planes of line II-II in FIG 5 and 7 ) of the jaw cylinder 1 shown in conjunction with jaw spacing adjustment means and drive means therefor;

3 is a sectional view taken along line III-III 2 ;

4 is a sectional view taken along line IV-IV 2 ;

5 is a sectional view taken along line VV 2 ;

6 is an enlarged, fragmentary sectional view taken along line VI-VI 2 showing a movable jaw part together with the fixed jaw;

7 is an end view of the jaw cylinder device, viewed in the direction of the arrow VII 2 ; and

8th FIG. 12 is a block diagram of the speed dependent jaw spacing adjustment system for the jaw cylinder apparatus 2 - 7 ,

DESCRIPTION OF THE PREFERRED Embodiment

folding station

The present invention is currently considered to be most applicable to the folding station of a rotary printing press which is adapted to print two or more webs simultaneously, for common processing to multi-page printed sheets, although of course only one paper web can be printed. As in 1 is shown schematically, the folding station shown by way of example F, a pair of feed rollers FN for introducing a continuous web or continuous webs W of printed paper in the folding station F by means of friction. Although in practice any required number of webs can be printed simultaneously and inserted one above the other into the folding station F, it will be assumed for the sake of simplicity of description that now only one printed web W is introduced into the folding station. In the prior art, it is common to fold the printed web in the longitudinal direction, for example by a former (not shown), which is arranged upstream of the folding station F.

The folding station F has a cutter cylinder _F1, a folding cylinder _F2, a jaw cylinder _F3, and a delivery fan _F4, for cutting the printed web W into sections PC, folding each web section around the middle of a print sheet and discharging the consecutive printing sheets , All cylinders F ₁ -F ₃ and the fan F ₄ are rotatably mounted between a pair of facing casing walls FF, one of which is shown. Below the discharge fan F ₄ , a discharge conveyor FC is arranged.

The cutting cylinder F ₁ has thereon one or more cutting knives F ₁₁ , two of which are shown, in circumferentially spaced apart positions with each knife extending parallel to the cutting cylinder axis. The folding cylinder F ₂ has on its surface on the circumference at regular intervals from each other a plurality of anvils or beds F ₂₂ for successive mating engagement with the cutting blades F ₁₁ on the cutting cylinder F ₁ on. Rows of retractable piercing pins F ₂₁ are also mounted on the surface of the folding cylinder F ₂ at positions immediately upstream of the anvils F ₂₂ with respect to the rotational direction of the folding cylinder indicated by arrows. The web W, which is placed around a part of the folding cylinder F ₂ , is detected by the successive rows of piercing pins F ₂₁ and, when the two cutting blades F ₁₁ on the cutting cylinder F ₁ successively with the successive anvils F ₂₂ on the folding cylinder F ₂ engage, cut across sections PC. The web sections PC then travel on the folding cylinder F ₂ , their leading edges being held in place by the piercing pins F ₂₁ .

The jaw cylinder _F3, which is shown as having the same diameter as the folding cylinder _F2, has defined in its surface a plurality of jaw cavities ₁₀ J, in this embodiment five, at uniform intervals around the circumference. Each web portion PC is guided by the folding cylinder F ₂ to a position opposite one of the jaw cavities J ₁₀ in the jaw cylinder F ₃ and its leading edge is released by the piercing pins F ₂₁ when the latter are then retracted into the folding cylinder F ₂ . At the same time, the middle part of the web section PC is pressed by one of the folding blade F ₂₃ on the folding cylinder F ₂ from its surface into one of the jaw cavities J ₁₀ in the jaw cylinder F ₃ . The inserted center portion of the web section FS is intended to be engaged therein by a set of a fixed jaw and a movable jaw, which will be described in more detail below. The jaws are not shown in this figure because of lack of space, but merely indicated by the capital letter J.

Then, the folding blade F ₂₃ is retracted with the jaws J disengaged, whereby the detected by the jaws path portion PC remains to be folded. While the folding cylinder F ₂ and the jaw cylinder F ₃ continue their rotation in opposite directions, the web portion PC is further transported from the folding cylinder to the jaw cylinder and thereby folded along the center line.

The discharge fan F ₄ , which is arranged between the jaw cylinder F ₃ and the discharge conveyor FC, has a plurality of guide vanes FA, which are mounted obliquely on the surface thereof to define pockets. The folded web sections or signatures PC fall sequentially by gravity from the jaw cylinder F ₃ into these pockets on the discharge fan F ₄ and out of these onto the discharge conveyor FC.

The hitherto described construction of the folding station F is largely conventional and does not include a feature of the present invention. The novel Features of the invention will become apparent in the course of the following detailed Description of the jaw cylinder, the sets of jaws together with its drive means, a jaw spacing adjustment, a drive mechanism for the jaw spacing adjustment and electronic controls for the automatic, speed-dependent adjustment of the jaw spacing seen.

jaw cylinder

• 1. Einem inneren Endteil 11, der ein Paar von inneren Endplatten 11_a und 11_b , 2 und 3, umfasst;
• 2. Einem äußeren Endteil 12, der ein Paar von äußeren Endplatten 12_a und 12_b , 2 und 4, umfasst;
• 3. Einem Kernteil 13, der den Kern des Falzklappenzylinders F₃ bildet und an dem sowohl der innere Endteil 11 als auch der äußere Endteil 12 für die unabhängige Rotation innerhalb von Grenzen angebracht sind.

Widely understood, the jaw cylinder F _{3 is formed} from the following three parts, which are each made in one piece:

• 1. An inner end part 11 that has a pair of inner end plates 11 _a and 11 _b . 2 and 3 , comprises;
• 2. An outer end part 12 that has a pair of outer end plates 12 _a and 12 _b . 2 and 4 , comprises;
• 3. A core part 13 which forms the core of the jaw cylinder F ₃ and on which both the inner end part 11 as well as the outer end part 12 for independent rotation within borders.

The inner end part 11 also includes several links 11 _c , where in 3 three are shown and which are the pair of inner end plates 11 _a and 11 _b connect and form parts of the surface of the jaw cylinder F ₃ . One of the opposite longitudinal edges of each link 11 _c is configured as a fixed jaw J ₁₃ , which forms part of the jaw means, which with reference to 3 be set out. Each of the inner end plates 11 _a and 11 _b has cut into these at least two slots 11 _d each of which extends radially away from its outer edge and just before its inner edge, which is the core part 13 surrounds, ends. The outer ends of all slots 11 _d be through caps 11 _c tightly closed. The purposes for which the slots 11 _d will become apparent from the following description of the jaw spacing adjustment.

The outer end part 12 also includes several links 12 _c , where in 4 three are shown and which are the pair of outer end plates 12 _a and 12 _b connect of approximately disc-like shape. With renewed reference to 3 it will be seen that each link 12 the outer end part between a link 11 the inner end part and a cap 11 _e is arranged and forms in this way parts of the surface of the jaw cylinder F ₃ . Each adjacent pair of link 11 the inner end part and link 12 the outer end portion are spaced from each other at the periphery of the jaw cylinder F ₃ to form one of the three jaw cavities J ₁₀ , in connection with 1 were set out. Each of the outer end plates 12 _a and 12 _b is in 4 as three radial slots 12 _d shown cut into it for purposes set forth in connection with the jaw spacing adjustment. The outer ends of the slots 12 _d are by caps 12 _e tightly closed.

The core part 13 has a section 13 _z larger diameter, with a pair of sections from opposite ends thereof 13 _e and 13 _f coaxially extending away with a smaller diameter. The section 13 _z with larger diameter of the core part 13 has several approaches 13 _d which extend radially from its opposite ends along the jaw cylinder axis. Each aligned pair of approaches 13 _d is interconnected by a link (not shown) which extends parallel to the jaw cylinder axis. The pair of sections 13 _c and 13 _f with smaller diameter of the core part 13 rotatably mounted thereon, the pair of inner end plates 11 _a and 1l _b of the inner end part 11 and the pair of outer end plates 12 _a and 12 _b the outer end part 12 on. A mounting plate 13 _g is on the left smaller diameter section 13 _f attached.

A pair of bearing journals 13 _a and 13 _b , which are rotatably supported by the pair of facing enclosure walls FF _a and FF _b , is connected to the sections 13 _e and 13 _f Coaxially coupled with smaller diameter. The right bearing journal 13 _e is attached via a set of bearings B _a and a bearing bush S _a to the right enclosure wall FF _a . The left bearing journal 13 _b is mounted on the left casing wall FF _b via a set of bearings B ₆ , a bushing S _c , another set of bearings B _c around the bushing S _c and another bearing bush S _b around the bearings B _c .

The left bearing journal 13 _b of the jaw cylinder F ₃ has a jaw cylinder drive gear GG which is fixedly attached at its end, which protrudes from the enclosure wall FF _b to the outside. Driven by a further drive wheel DG, the drive gear GG serves to transmit rotation to the jaw cylinder F ₃ . The Falzklappenzylinderantriebsrad GG and the other drive wheel DG have the form of a helical gear, as it has additional functions in connection with the drive mechanism 30 for the jaw spacing adjustment 20 should perform.

Folding flaps and jaw drive means

Either 2 as well as 3 show a series of movable jaw parts J ₁₂ in each of the jaw cavities J ₁₄ . The movable jaw members J ₁₂ are mounted on a jaw carrier shaft J ₁₄ in a manner to be described in more detail below for common pivotal movement in and from web section folding engagement with the fixed jaw J ₁₃ . The jaw carrier shaft J ₁₄ itself is through the pair of outer end plates 12 _a and 12 _b the outer end part 12 rotatably mounted, how better 4 evident. For ease of description, each row of movable jaw members will hereinafter be referred to collectively as a movable jaw and individually as movable jaw members, and in both cases the same reference character J _{12 will be} used.

6 Best illustrates how each movable jaw member J _{12 is} attached to the jaw carrier shaft J ₁₄ . Each movable jaw member J ₁₂ is mounted or otherwise secured to a movable jaw base member J ₁₉ , which in turn rotatably attaches to the jaw carrier shaft J ₁₄ via a pair of axially spaced plain bearings, which are not visible in this sectional view. A spring seat J ₂₀ is fixed or otherwise attached to the jaw carrier shaft J ₁₄ for conjoint rotation therewith, and a compression coil spring J ₂₁ is mounted between the movable jaw base J ₁₉ and the spring seat J ₂₀ on one side of the jaw carrier shaft. On the other side of the jaw carrier shaft J ₁₄ , the movable Falzklappenbasiselement J ₁₉ is biased by the compression spring J ₂₁ via a member J ₂₂ made of wear-resistant material in an abutting position against the spring seat J ₂₀ . This figure also shows a torsion spring J ₁₈ which is incorporated into the jaw carrier shaft J _{14 to} bias the same so as to be shown in FIG 6 is rotated clockwise.

The rotation of the folding jaw carrier shaft J ₁₄ in a representation as shown 6 counterclockwise direction, against the force of the torsion bar spring J ₁₈ , is therefore transferred via the spring seat J ₂₀ and the compression spring J ₂₁ on the movable base member J ₁₉ , whereby the associated movable jaw member J ₁₂ moves to the fixed jaw J ₁₃ out , On the other hand, as the jaw carrier shaft J ₁₄ rotates clockwise, the spring seat J ₂₀ directly and rigidly acts on the movable jaw base member J ₁₉ to cause the movable jaw member J _{12 to} retract from the fixed jaw J ₁₃ .

Again on 2 Referring to Fig. ₁₄ , the jaw carrier shaft J ₁₄ rotatably extends through the right outer end plate 12 _a and has a crank arm J ₁₅ fixedly attached to its projecting end. The crank arm J ₁₅ has a crank pin on which a cam follower roller J _{16 is} rotatably mounted for rolling engagement in a groove in a jaw drive cam J ₁₇ of an annular shape. The jaw drive cam J ₁₇ is immovably mounted on the enclosure wall FF _a via a bearing bush S _a .

Thus, with the rotation of the jaw cylinder F _3, the cam follower roller J _{16 will} roll along the groove defined by the jaw drive cam J ₁₇ and thereby cause the crank arm J _{15 to} rotate bidirectionally. The bidirectional rotation of the crank arm J ₁₅ is transmitted directly to the jaw carrier shaft J ₁₄ and from there, as in connection with 6 has been set, on the movable Falzklappenbasiselemente J ₁₉ , spring seats J ₂₀ and compression springs J ₂₁ on the movable jaw members J _12th When the movable jaw J ₁₂ is rotated all the way to the fixed jaw J ₁₃ , the compression springs J ₂₁ are compressed to different degrees depending on the thickness of the folded middle portion of the web portion PC caught therebetween. The differential amount of compression of the compression springs J ₂₁ determines different amounts of energy stored thereby to act on the respective movable jaw members J ₁₂ to cause them to press the web section PC against the fixed jaw J ₁₃ .

jaw spacing

As mentioned, the fixed jaws are J ₁₃ on the links 11 of the inner end part 11 as in 3 formed while the movable jaws J ₁₂ through the pair of outer end plates 12 _a and 12 _b the outer end part 12 as in 4 are rotatably mounted. It was also said that the inner end part 11 and the outer end part 12 the jaw cylinder F ₃ relative to the core part 13 are independently rotatable. The spacings between the movable jaws J ₁₂ and the fixed jaws J ₁₃ are therefore by varying at least one of the angular positions of the inner end portion 11 and the outer end part 12 at the core part 13 adjustable. The inner end part 11 and the outer end part 12 in this embodiment of the invention, both simultaneously through the jaw spacing adjustment 20 subjected to angular displacement in opposite directions.

For such a simultaneous angular displacement of the inner end part 11 and the outer end part 12 and consequently the movable jaws J ₁₂ and the fixed jaws J ₁₃ become two camshafts 14 and 15 . 2 , which extend parallel to the jaw cylinder axis and which are arranged at equal intervals thereof. The camshaft 14 is formed to the angular displacement of the inner end portion 11 and hence the fixed jaws J ₁₃ relative to the core part 13 to effect and is therefore referred to in the sequence as a camshaft for fixed jaws. The other camshaft 15 is then referred to in the sequence as the movable jaw camshaft which is adapted to angular displacement of the outer end portion 12 and hence the movable jaws J ₁₂ relative to the core part 13 to effect. The camshaft 14 for fixed jaws and the camshaft 15 for movable jaws are each through the lugs 13 _d of the core part 13 via bearings B _d and B _c or through the mounting plate 13 _g stored above bearings B _f and B _g .

As by reference to 3 , in addition to 2 To be better understood, the camshaft extends 14 for fixed jaws through the slots 11 _d in the pair of inner end plates 11 _d and 11 _b and with play through the slot 12 _d in an outer end plate 12 _b , The camshaft 14 for fixed jaws has two cams 16 for fixed jaws eccentrically mounted thereon. The cams 16 for fixed jaws are rotatable in annular shoes 18 taken in turn, in the slots 11 _d in the inner end plates 11 _a and 11 _b are absorbed and forced to become linear to the slots 11 _d and in directions orthogonal to radii of the inner end plates 11 _a and 11 _b to move. As a result, the camshaft acts 14 for fixed jaws, when bidirectionally powered, over the cams 16 for fixed jaws and the shoes 18 on the inner end part 11 causing angular displacement of the fixed jaws J ₁₃ with respect to the core member 13 comes.

A reference to both 2 as well as 4 will make it clear that the camshaft 15 for movable jaws similar to the outer end part 12 acts to cause angular displacement of the movable jaws J ₁₂ . The camshaft 15 for movable jaws extends through the slots 12 _d in the pair of outer end plates 12 _a and 12 _b and with play through the slots 11 _d in the pair of inner end plates 11 _a and 11 _b , The camshaft 15 for movable jaws has two cams 17 for movable jaws mounted eccentrically on it. These cams 17 be in ring-shaped shoes 19 rotatably received, which in turn in the radial slots 12 _d in the outer end plates 12 _a and 12 _b for linear movement along these are slidably added. The bidirectional rotation of the camshaft 15 for movable jaws is therefore on the cam 17 for movable jaws and the shoes 19 in the bidirectional angular displacement of the outer end part 12 around the core part 13 implemented, whereby the movable jaws J ₁₂ are moved toward the associated fixed jaws J ₁₃ or away.

Outward from the mounting plate 13 _g outstanding, as in 2 , assign both the camshaft 14 for fixed jaws as well as the camshaft 15 for movable jaws pinion 21 and 22 which are firmly attached to it. As well as in 5 is shown, these are pinions 21 and 22 no matter what the number of teeth, the pitch diameter, etc., and both mesh with a jaw spacing adjustment wheel 23 which is coaxially fixed to the above bearing bush S _c on the enclosure wall FF _b . Also on this bushing S _c , on the outside of the skirt wall FF _b , is another jaw spacing adjustment wheel 24 coaxially attached, which is a helical gear with the same pitch diameter as said Falzklindelenzylinderantriebsschraubenrad GG on the jaw cylinder journal 13 _b is. The teeth of this jaw spacing adjustment wheel 24 however, are curved in a direction opposite to that of the teeth on the jaw cylinder drive gear GG. The jaw spacing adjustment wheel 24 is through the drive mechanism 30 driven, which is now explained in more detail.

Accordingly, turn during the rotation of the wheel 23 in one of the two directions the pinions 21 and 22 in the same direction and at the same speed together with the camshaft 14 for fixed jaws and the camshaft 15 for movable jaws. These camshafts 14 and 15 transfer their rotation to the inner end part 11 the jaw cylinder F ₃ on the cam 16 for fixed jaws and the shoes 18 or on the outer end part 12 the jaw cylinder over the cams 17 for movable jaws and the shoes 19 , The result is the rotation of the inner end part 11 and the outer end part 12 relative to the core part 13 at the same angle, but in opposite directions, which results in a change in the spacing between movable jaws J ₁₂ and fixed jaws J ₁₃ in any position of the movable jaws relative to the fixed jaws.

Drive mechanism for folding jaw spacing adjustment

2 best illustrates the drive mechanism 30 to the jaw spacing position, although this one too 7 evident. This also includes a bidirectional electric motor 31 which is preferably a stepping motor of a type known per se, hereinafter referred to as a jaw spacing adjustment motor or simply an adjustment motor. The jaw spacing adjustment motor 31 who at 33 on a larger bracket 28 is attached to the enclosure wall FF _b by means of bracket, carries on its armature shaft, a drive pinion 32 that with a powered wheel 28 _f combs. This driven wheel is fixed to a threaded spindle 28 _c attached, rotatable by a nut 28 _e which is not rotatable by the bracket 28 is stored. Therefore, with bidirectional rotation of the adjustment motor 31 , the threaded spindle 28 _c not only rotate, but also move axially toward or away from the skirt wall FF _b in a direction parallel to the axis of the jaw cylinder F ₃ . It is understood that the drive pinion 32 has a sufficient axial design to the driven wheel 28 _f over the entire path of the threaded spindle 28 to stay engaged.

The threaded spindle 28 is with the end with a movable socket 28 _b coupled to a straight splined shaft 28a is attached, which is cantilevered on the enclosure wall FF _b . The threaded spindle 28 is rotatable, but is at axial displacement relative to the movable sleeve 28 _b prevented. Accordingly, it is only the linear movement of the threaded spindle, which on the movable socket 28 _b is transmitted and causes these on the straight wedge arm shaft 28 _a moved linearly backwards and forwards. Rotatable on the movable socket 28 _b attached are two helical gears 25 and 26 of substantially one-piece construction, which are axially movable together with the movable sleeve. The helical wheels 25 and 26 with the jaw cylinder drive screw GG and the jaw spacing adjusting screw wheel, respectively 24 ,

Electronic regulations

As in 8th is illustrated in the form of a block diagram, the electronic control system according to the invention is adapted to the jaw spacing adjustment 20 via the adjustment drive mechanism 30 to regulate. The control system includes a printing press speed circuit 50 used as a printing press speed pulse generator 51 and a pulse counter 52 is shown comprehensively. In practice, the printing press speed generator 51 have the form of a rotary encoder mounted on any rotating part of the printing press, for providing a series of printing press speed pulses at a rate proportional to the operating speed of the printing machine. The pulse counter 52 may then count the upcoming print engine speed pulses during each pre-assigned time period and output a press speed signal indicating the press speed at that time. The printing press speed signal becomes a jaw spacing adjustment circuit 90 fed.

Also, the jaw spacing adjustment circuit 90 fed to a jaw spacing signal from a jaw spacing circuit 70 indicating the current actual jaw spacing. This circuit 70 is a combination of a jaw spacing pulse generator 71 and a computing unit 71 shown. Again, the jaw spacing pulse generator 71 have the form of a bidirectional incremental encoder, the bidirectional stepper motor 31 the jaw spacing adjustment drive mechanism 30 for providing a series of jaw spacing pulses indicative of how the stepper motor is associated 31 the jaw spacing adjustment 20 drives to change the spacing between movable jaws J ₁₂ and fixed jaws J ₁₃ . By counting the jaw spacing pulses bidirectionally, the computing unit determines 72 the current actual jaw spacing at any phase of the pivoting movement of the movable jaws J ₁₂ and indicates the jaw spacing signal indicative of that jaw spacing for transmission to the jaw spacing adjustment circuit 90 out.

Incidentally, the arithmetic unit should 72 remain switched on, even if the printing press is not in operation. If the press is subsequently put into operation, the arithmetic unit 72 then provide the jaw spacing signal indicative of the jaw spacing that existed when machine operation was completed.

By inputting both the print engine speed signal from the print engine speed circuit 50 as well as the jaw spacing signal from the jaw spacing circuit 70 causes the jaw spacing circuit 90 that the stepper motor 30 . 2 , For Optimum Falzklappenbeabstandung at the current operating speed of the printing press is regulated fed with energy. The jaw spacing adjustment circuit 90 includes a jaw spacing adjustment signal generator 91 in which not only the printing press speed circuit 50 and the jaw spacing circuit 70 but also an input device 100 for entering data indicating the thickness of the folding station F, 1 , to be handled railways or trains are connected.

In particular, the input device 100 for inputting both the thickness of the paper used and the number of printed sheets to be overlaid on the folding station for common cutting and folding into signatures. When the jaw spacing adjustment signal generator 91 is preprogrammed to select from a variety of known paper thicknesses, the paper thickness data may be entered in the form of the trade name of the paper or any commodity number or designation assigned thereto. Similarly, when the jaw spacing adjustment signal generator 91 is preprogrammed to select from among a plurality of possible numbers of trajectories to be superimposed, the trajectory data is entered in the form of the pages of the signatures to be produced.

• * ×10.000 Druckbögen pro Stunde

Also to the jaw spacing adjustment signal generator 91 connected is a memory 92 in which a jaw spacing table is stored as shown below. The table indicates predetermined optimum jaw spacings for various combinations of different predetermined press speeds and various predetermined numbers of webs to be printed simultaneously and processed together at the folder assuming that the paper used is the standard thickness. The press speeds are expressed in terms of the number (unit is 10,000) of printed sheets per hour produced, and the number of sheets is indicated as pages per sheet. How does the jaw spacing adjustment signal generator 91 This table will be apparent in the course of the following description of the operation. BACKENBEABSTANDUNGSTABELLE PRESSURE MACHINE SPEED * PAGES EVERY PRINTED BOW 4 8th 12 16 20 24 ......... 40 44 48 1 0.9 1.2 1.5 1.7 1.9 2.1 ......... 3.1 3.3 3.6 2 0.9 1.2 1.5 1.7 1.9 2.1 ......... 3.1 3.3 3.6 3 0.9 1.2 1.5 1.7 1.9 2.1 ......... 3.0 3.3 3.6 4 0.9 1.2 1.4 1.7 1.9 2.1 ......... 3.0 3.3 3.6 5 0.9 1.2 1.4 1.6 1.9 2.1 ......... 3.0 3.3 3.6 6 0.9 1.1 1.4 1.6 1.8 2.1 ......... 3.0 3.2 3.6 7 0.9 1.1 1.4 1.6 1.8 2.0 ......... 3.0 3.2 3.5 8th 0.9 1.1 1.4 1.6 1.8 2.0 ......... 2.9 3.2 3.5 9 0.8 1.1 1.4 1.6 1.8 2.0 ......... 2.9 3.2 3.5 10 0.8 1.1 1.4 1.6 1.8 2.0 ......... 2.9 3.2 3.5 11 0.8 1.1 1.3 1.6 1.8 2.0 ......... 2.9 3.1 3.5 12 0.8 1.1 1.3 1.6 1.8 2.0 ......... 2.9 3.1 3.4 13 0.8 1.1 1.3 1.5 1.8 2.0 ......... 2.9 3.1 3.4 14 0.8 1.1 1.3 1.5 1.7 1.9 ......... 2.9 3.1 3.4 15 0.8 1.0 1.3 1.5 1.7 1.9 ......... 2.8 3.1 3.4 16 0.8 1.0 1.3 1.5 1.7 1.9 ......... 2.8 3.0 3.4 17 0.8 1.0 1.3 1.5 1.7 1.9 ......... 2.8 3.0 3.3 18 0.8 1.0 1.2 1.5 1.7 1.9 ......... 2.8 3.0 3.3 19 0.8 1.0 1.2 1.4 1.7 1.9 ......... 2.8 3.0 3.3 20 0.7 1.0 1.2 1.4 1.6 1.8 ......... 2.7 2.9 3.2

• * × 10,000 signatures per hour

The output of the jaw spacing adjustment signal generator 91 is to a motor driver circuit 93 and from there to a stepper motor 31 . 2 , the jaw spacing adjusting drive mechanism 30 connected. The motor driver circuit 93 feeds the stepper motor 31 controllable with energy for rotation in one of two opposite directions, whereby the jaw spacing adjustment 20 adjusting the jaw spacing according to the concrete combination of the actual operating speed of the printing press and the number of webs to be processed one above the other. The jaw spacing can also be adjusted for the thickness of the paper used, even if it deviates from the norm, as will be seen from the following description of the operation.

business

Before the beginning of each print job, the operator or machine operator may prepare both paper thickness data and data on the number of sheets or signature pages from the input device 100 in the jaw spacing adjustment signal generator 91 enter. The web of paper W is through the folding station F as in 1 to introduce presented. When the printing press is put into operation, the cutter cylinder _F1, folding cylinder _F2, jaw cylinder _F3 and delivery fan F of ₄ all rotate at the same peripheral speed. The printed web W is moved over the folding cylinder F ₂ and cut by the cutting blade F ₁₁ on the cutting cylinder F ₁ by cooperation with the anvils F ₂₂ on the folding cylinder in successive sections PC.

In a position that is at an angle of about three-fifths of a full turn of the folding cylinder F ₂ is spaced from the position where the web W is cut as described above, the middle part of each web section PC is placed opposite one of the jaw cavities J ₁₀ in the jaw cylinder F ₃ . One of the folding blades F ₂₃ on the folding cylinder F ₂ will then press this central part of the web section PC into the jaw cavity J ₁₀ . Then, the movable jaw J ₁₂ , which is mounted in this jaw cavity, turn to the fixed jaw J ₁₃ , wherein the inserted middle part of the web section PC is pressed together with the folding blade F ₂₃ against the fixed jaw. The movable jaw J ₁₂ is actuated such that the crank arm J _{15 is} caused on the jaw carrier shaft J ₁₄ by the jaw drive cam J ₁₇ , as shown 6 to rotate counterclockwise, with which the cam follower roller J ₁₆ moves in constant rolling engagement during the rotation of the jaw cylinder F ₃ . The jaw carrier shaft J ₁₄ rotates with the crank arm J ₁₅ against the force of the built-in torsion bar spring J _18th

As by recent reference to 6 will be appreciated, the rotation of the jaw carrier shaft is transmitted J ₁₄ anti-clockwise via the spring seats _J20, compression springs J ₂₁ and J ₁₉ Falzklappenbasiselemente to the movable jaw parts J _12th The movable jaw members J ₁₂ will in this way elastically press the middle part of the web section PC against the fixed jaw J ₁₃ , while the compression springs J _{21 are} compressed to different degrees, depending on the total thickness of the doubled middle part of the web section PC and the folding blade F ₂₃ , the latter is still covered in the former.

With continued rotation of the folding cylinder F ₂ and the jaw cylinder F ₃ , the folding blade F ₂₃ moves out of the jaw cavity J ₁₀ in the jaw cylinder, is retracted into the folding cylinder and leaves the doubled middle part of the web section PC. Then, the movable jaw J _{12 is} caused by the compression springs J ₂₁ to press the middle part of the web section PC against the fixed jaw J ₁₃ and thus to fold this along its center line. Then, still with the continuation of the rotation of the folding cylinder F ₂ and the jaw cylinder F ₃ , the web section PC releases from the folding cylinder and is completely laid over the jaw cylinder.

As the folded web section PC travels over the jaw cylinder F ₃ , the jaw carrier shaft J ₁₄ rotates clockwise as shown by the jaw drive cam J ₁₇ as shown 6 , The torsion spring J ₁₈ supports such a clockwise rotation of the jaw carrier shaft J ₁₄ . The movable jaw J ₁₂ , which rotates clockwise with the jaw carrier shaft J ₁₄ , releases the folded web portion PC and thus allows it to fall by gravity from the surface of the jaw cylinder F ₃ into one of the pockets passing through the oblique vanes FA 1 be defined on the discharge fan F ₄ . The vanes FA are angled with respect to this direction of rotation of the discharge fan F ₄ so that the folded web portion PC subsequently slides down one of the vanes onto the underlying discharge conveyor FC to thereby be transported to a shipping point.

The jaw spacing adjustment system according to the invention is automatically started up after the start of printing. The printing machine speed circuit 50 . 8th , the operating speed of the printing machine will be determined while the jaw spacing circuit 70 will calculate the actual spacing between fixed and movable jaws. In particular, at the printing press speed circuit 50 the pulse counter 52 the output pulses of the printing machine speed pulse generator 51 during each of consecutive, pre-assigned periods of time and output the machine speed indicative press speed signal in real time.

At the jaw spacing circuit 70 counts, however, the arithmetic unit 72 also the jaw spacing pulses from its generator 71 and further calculates the actual jaw spacing for a particular phase of operation of the jaw spacing adjustment drive means 30 Such a phase being detectable from the upcoming jaw spacing pulses. The arithmetic unit converts the resulting jaw spacing signal to the jaw spacing adjustment signal generator 91 which also includes the press speed signal from the print engine speed circuit 50 is supplied.

Each time the inputted printing machine speed signal is renewed, the jaw spacing adjustment signal generator becomes 91 by reading the at the concrete operating speed of the printing press and the concrete number of jointly processed expectant webs to be produced Falzklappenbeabstandung from the Falzklappenbeabstandungstabelle in the memory 92 re act.

L

= die aktuelle Soll-Falzklappenbeabstandung;

L₀

= die aus dem Speicher ausgelesene Falzklappenbeabstandung;

t

= die Dicke des aktuell verwendeten Papiers; und

t₀

= die Normpapierdicke.

Under certain circumstances, the thickness of the paper used by the input device 100 is different from the standard thickness on the basis of which the saved table was created. In such cases, the jaw spacing adjustment signal generator calculates 91 the jaw spacing to be provided for this paper thickness at the current operating speed of the printing press and for the current number of webs, by the equation: L = L 0 x (t / t 0 ) in which

L

= the current desired Falzklappenbeabstandung;

L ₀

= the jaw spacing read from the memory;

t

= the thickness of the currently used paper; and

t ₀

= the standard paper thickness.

Thereafter, the jaw spacing adjustment signal generator goes on 91 to compare the thus calculated desired jaw spacing with the actual jaw spacing, at this time by the jaw spacing signal from the jaw spacing circuit 70 is specified. If the difference between the desired and actual jaw spacing is greater than a preset limit, the jaw spacing adjustment signal generator operates 91 in that the motor driver circuit 93 the jaw spacing adjustment motor 31 fed with energy. This motor will then rotate in such a direction and angle as to optimize the jaw spacing at the current printing press speed and at the current number of superimposed webs.

The required angle of rotation of the jaw spacing adjustment motor 31 in the required direction is by the threaded spindle 28 in the linear movement of the socket 28 _b on the straight wedge arm shaft 28 _a implemented. The helical wheels 25 and 26 will be axial with the bush 28 _b move. The helical gear is engaged with the jaw cylinder driving helical gear GG secured against axial displacement 25 after axial displacement also experience an angular displacement, together with the second helical gear 26 ,

The second helical wheel 26 in turn is with the jaw spacing adjustment screw wheel 24 engaged, so that this wheel after linear movement of the second helical gear 26 also turns. Further, since the second helical gear 26 in turn by the Falzklappenzylindrrad GG with the first helical gear 25 shifted by an angle, this angular displacement of the second helical gear also on the Falzklappenbabstandungseinstellungsrad 24 transfer. The resulting rotation of this wheel 24 is on the sleeve S _c on the other jaw cylinder drive wheel 23 and from there to the pinions 21 and 22 on the camshaft 14 for fixed jaws and the camshaft 15 transferred for movable jaws.

With reference to both 2 and 3 guides the rotation of the camshaft 14 for fixed jaws on the one hand to eccentric revolutions of the two cams 16 for fixed jaws, which are non-rotatably mounted thereon. The cams 16 for fixed jaws that are inside the annular shoes 18 rotate, cause the shoes linear the slots 11 _d in the pair of inner end plates 11 _a and 11 _b of the inner end part 11 along the jaw cylinder and in directions orthogonal to the radii of the inner end plates. The shoes work 18 on the inner end plates 11 _a and 11 _b and cause the entire inner end part 11 the jaw cylinder at the jaw cylinder core part 13 turns in one direction.

The rotation of the camshaft 15 for movable jaws on the other hand leads analogously to eccentric revolutions of the two cams 17 for movable jaws, 2 and 4 which are non-rotatably attached thereto. These cams 17 turn inside the ring-shaped shoes 19 and cause these to become linear the slots 12 _d in the pair of outer end plates 12 _a and 12 _b the outer end part 12 along the jaw cylinder and in directions orthogonal to the radii of the outer end plates. The complete outer end part 12 the jaw cylinder then rotates in the other direction on the jaw cylinder core part 13 ,

When the inner end part 11 the jaw cylinder and the outer end part 12 the jaw cylinder on the jaw cylinder cylinder core part 13 thus rotating in opposite directions, so do the fixed jaws J ₁₃ and the movable jaws J ₁₂ at the inner end portion 11 or the outer end part 12 of the jaw cylinder are stored. The spacing between the jaws J ₁₂ and J ₁₃ was thus adjusted and optimized for the current press speed, for the current number of co-processed webs, and for the current thickness of paper used.

Again on 8th Referring to the jaw spacing pulse generator 71 in the form of a bidirectional incremental encoder, a series of jaw spacing pulses representing the rotations of the stepping motor 31 specify. The arithmetic unit 72 responds to each coming jaw spacing pulse by adding or subtracting one from the count value present at the beginning of the current jaw spacing adjustment routine. The arithmetic unit 72 then proceeds to calculate from the modified pulse count the actual jaw spacing, which has been adjusted as described above, and the jaw spacing adjustment signal generator 91 to supply the jaw spacing signal, which suggests this actual jaw spacing. The jaw spacing adjustment signal generator 91 Again, the actual Falzklappenbeabstandung with the desired Falzklappenbeabstandung compare. The same duty cycle is repeated if the result of the comparison exceeds the preset limit until the difference falls below the limit.

Notwithstanding the foregoing detailed disclosure, it is not intended to limit the present invention by the specific illustrations of the accompanying drawings or the description thereof. For example, the input device 100 . 8th Not required for those press systems where only one web or a predetermined number of webs are to be processed and where paper of only a known thickness is always to be used. The above speed and thickness dependent jaw spacing table is then modified and simplified, with everything in the memory 92 is to be stored, in this case, the desired Falzklappenbeabstandungen are at the different speeds of the sheet production. Furthermore, as indicated by the dashed outline 8th is specified, the printing machine speed pulse counter 52 the printing machine speed circuit 50 , the arithmetic unit 72 the jaw spacing circuit 70 and the jaw spacing adjustment signal generator 91 and the memory 92 the jaw spacing adjustment circuit 90 be integrated into an electronic processing unit C.

These and other obvious modifications, amendments and adaptations illustrated embodiment are intended in the foregoing disclosure. Consequently, it is it is convenient to set forth the invention broadly and in a manner the real meaning or the actual one The scope of the following claims equivalent.

Claims (4)

A speed-dependent jaw spacing adjustment system for a jaw cylinder (F ₃ ) at the folding station (F) of a web-fed rotary printing press where at least one printed paper web (W) is cut into successive sections (PC) and each web section is folded into a signature sheet, the jaw cylinder being a fixed and a folding jaw cylinder a movable jaw (J ₁₃ and J ₁₂ ), which on separate, independently movable parts ( 11 and 12 ) of the jaw cylinder, the movable jaw being movable relative to the independently movable parts of the jaw cylinder toward and away from the fixed jaw, for engaging and folding each web portion when the center portion thereof is inserted between the fixed and movable jaws; wherein the speed dependent jaw spacing adjustment system includes jaw spacing adjustment means (10). 20 ) with the individually moving parts ( 11 and 12 ) of the jaw cylinder for moving the fixed and movable jaws toward and away from each other to adjustably vary the spacing therebetween in any operative phase of the movable jaw relative to the fixed jaw, and drive means (15); 30 ) coupled to the jaw spacing adjustment means for bidirectionally driving the same, characterized in that it further comprises a printing press speed circuit ( 50 ) for providing a printing machine speed signal indicative of the speed with which the web is currently being fed to the folding station, a jaw spacing circuit (US Pat. 70 ) for providing a jaw spacing signal indicative of an actual spacing between the fixed and movable jaws, and a jaw spacing adjustment circuit (US Pat. 90 ) with inputs connected to the printing machine speed circuit ( 50 ) and to the jaw spacing circuit ( 70 ) for providing, depending on the printing press speed signal and the jaw interruption a jaw spacing adjustment signal for adjusting jaw spacing corresponding to the current press speed, the jaw spacing adjustment circuit having an output to be coupled to the drive means (Fig. 30 ) to cause them to operate the jaw spacing adjustment means ( 20 ) in response to the jaw spacing adjustment signal. A speed-dependent jaw spacing adjustment system according to claim 1, characterized in that the jaw spacing circuit ( 70 ) with the drive means ( 30 ) for detecting the actual spacing between the fixed and movable jaws (J ₁₃ and J ₁₂ ). A speed-dependent jaw spacing adjustment system according to claim 1, characterized in that the jaw spacing adjustment circuit (15) 90 ) has another input which is connected to an input means ( 100 ), at which data is to be entered, which indicate how many webs are to be processed together, and that the jaw spacing adjustment circuit for transmission to the drive means ( 30 ) outputs a jaw spacing signal that outputs a desired jaw spacing that accommodates both the speed at which the web or webs are processed and the number of webs that are processed together. A speed-dependent jaw spacing adjustment system according to claim 3, characterized in that the jaw spacing adjustment circuit (10) 90 ) a memory ( 92 ) for storing a table indicating desired jaw spacings for various combinations of a number of different speeds at which the web or webs are to be processed and a series of different numbers of webs to be processed simultaneously.